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Oct. 9 I923. 1,470,562 I B. HALL VARIABLE SPEED MECHANISM Filed June 17, 1918 6 Sheets-Shet 1 Iii/9.1.

Oct. 9, 1923. 1,470,562 B.HALL

. VARIABLE SPEED MECHANISM Filed June 17, 1918 6 Sheets-Sheet 3 Inventor.- 13230 era/6Z5 Hail by Z QM, W ,aiig

Oct. 9-, 1923. 1,470,562

B. HALL VARIABLE SPEED MECHANISM Filed June 17, 1918 6 Shets-Sheet 4 Invenior; 0 Dick eZZHaZZ.

B.HALL

VARIABLE SPEED MECHANISM Filed June 17, 1918 e Sheets-Sheeb 5 B.HALL

VARIABLE SPEED MECHANI SM Fil ed June 17, 1918 6 Sheets-Sheet 6 '49 g 47 lavish/i02 fBi/cBiwi/el Hail. I

Patented Oct. 9, 1923.

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BICKNELL HALL, (3F ABINGTON, HEASSACHUSETTS, ASSIGNOE T HJLLL 00., OF BOSTON,

MASSACHUSETTS, A CORIORATIGN 0F I'JIASSACHUSETTS.

VARIABLE-SPEED IVEECHANISIVL Application filed June 17, 1918.

To (EU whom it may concern:

it l-ZnoWn that L BICKNELL HALL a citizen of the United States and a resident of .a kbington, in the county of Plymou h and Skate ojt Massachusetts, have invented an improvement in Variable-Speed Mechanism, of which the following description, in connection with the accompanying drawings, is a specification, like characters on the drawings representing; like parts.

This invention relates to variable speed mechanism. the object thereof being to im prove simplify and render the same more compact. The present application is a fil ng, with the same disclosure, of my an plication Serial No, %,100, a renewal of Serial No. 507,6l6, originally tiled July lat, 1900.

The nature of my invention will best a'p pear from a. description of one cmbmlimeut thereof selected for illustrative purposes and shown in the. accompanying drawings wherein-- Fig. 'l is a side elevation With the casings; i section of a speed varying mechanism embodying my invention;

Fig. 2 is a vertical, longitudinal, central section oi the mechanism shown in Fig. i;

l i 3 is a section taken at right and E to that of 2;

Fig. 4k is an end elevation representing in full and dotted lines one torm oi means to changing the position of the adjustable disic bearings;

Fig. is a vertical transverse section. taken. through one. oi" the adjustable disk bcarinq's and the gear for ai'ljustinothe same;

hip. 6 is a perspective view of the ma n or drive shaft;

Fig. 7 is a. transverse section upon ti line 7-7 of F l and representing: the r: lation cit one set of gear se g mcnt to adjacent fixed bearing when aid fixed d bean-i119; adjacent adjusta disk hearing and its transmission ring are concent rically arranged Fig; 8 is a similar View of .raid parts wh n said 1' "d disk bearing and adjustable d iiboaring and its transmission ring are ecccntrically arranged;

Figs. 9 and 10 are views similar to Figs. 7 and S. but representing the relation of the. 1 x M i l a an serene. srt 0| 5.. a1 stainin to we a. disk bearing (itjfiCQllll thereto;

Serial No. 240,325.

Figs. 11 to 18 inclusive are diagrams representing; the path of movement of one of the fixed disk bearings and its gear sen monts with respect to the internal fixed gear during a single cycle of said fixed disk bearing;

li ies. 19 to 26 inclusive are diagrams representing the path of movement of the other fixed disk bearing and its gear segments during; the corresponding. cycle of said other fixed disk bearing;

Figs. 27 29 and 31 are diagrams represeatingcorresponding phases of one of the tired disk bea and its gear segments in ilil'lerent positions of adjustment of the adjacent adjustable disk bearing;

ip s. 28, and are diagrams of corresponding;- phases of the other fixed disk bear inn and its gear segments in the same several positions of adjustment of the correspending; adjustable disk bearing; and

l i n's, 83 and bl represent in side elevation and end view respectively means for all justing the position of the fixed internal ears Rt. rruig first to lfigs. l. to 6 lnclusive,

upon a suitable base (not shown) are erected two end standard l 2 herein shown ascir cumterentially grooved to receive a cylin drical casing preferably entirely enclos ing; the mechanism excepting at the point from whence power is delivered. lVithin hearings in said standard is mounted a drive shaft 4; having keyed thereon a pulley 53. to which povrer may be applied from any suitable source, whereby the shaft may be driven at a constant speed in one direction. A shown most clearly in Fig. 6, the drive shaft has formed with or test thereon eccez-itric seats 6, 6, 7 7. While my inventioi'i may be embodied in a coi'istruction having; a single fixed disk bearing, a single ad justable oisk bearing and related parts to be hereinafter described preferably .I cum ploy a plurality and in the present embodiment of the invention a pair 01. each of said parts. inasmuch as in this embodiment of the invention *arious parts are duplicated. it will be necessary to describe in detail but one set of parts excepting in so tar it is essential to make clear the differ. circumferential positions of certain of a member of said sets of parts.

The eccentric seat 6 is rectangular and square While the eccentric seat 7 is rectangw lar but oblong. Seated upon the eccentric seat 6 is an eccentric disk 8. If desired the disk 8 may be integrally formed with the seat 6. Upon the inner face of the disk 8 is an annular flange 9 or other suitable formation. Upon the oblong seat 7 is positioned a slotted disk bearing 10, the diametral slot 11 thereof being of such length as to permit the shifting of the disk bearing 10, so as to vary its eccentricity with reference to the drive shaft 4. While any suitable means may be employed to vary the eccentricity thereof, preferably I form with or attach to one of the walls of the slot 11 a rack 12 meshing with an elongated pinion 13 mounted within the drive shaft 4;, which for that purpose is made hollow for a portion of its length,'as -represented in Fig. 3.

. Inasmuch as the eccentricity of the disk 8' is unchangeable, I shall herein term the said part the fixed disk bearing, and as the eccentricity. of the slottedbearing 10 may be varied or eliminated, I shall term the same the adjustable disk bearing.

Surrounding the fixed bearing 8 and fixedly attached to the inner face of the standard 1 by bolts 14 or otherwise is an internal gear or annular rack 15.

Upon the annular flange 9 of the fixed disk bearing 8, I mount one or more herein toothed gear segments, shown most clearly in F igs. 7 and'8, and therein lettered a, b, o and (Z, four being preferably employed. The said gear segments are of any suitable cir- ,cumferential extent and are loose upon said tered. Each of said gear segments is provided with an angular spoke or lug 16, the foot liwhereof serves as the point of pivotal attachment thereof to its segment. The upright portion of-each spoke or lug may therefore shifted from time to time as hereinafter described in varying the eccentricity of the adjacent adjustable eccentric bearing,

Loose upon the adjustable eccentric bearing 10 is a transmission ring 18, herein represented as made in two parts for convenience in assembling. Each part of said ring is provided with an annular seat 19, thus affording a flange. 20, the two flanges over lapping the adjustable disk bearing 10 as represented and confining the ring thereon. The two parts of the said transmission ring are suitably secured together as by means of screws 21. That portion of the transmission ring 18 that is positioned next the gear segments at, b, 0 and (l is provided upon its face adjacent said gears with a suitable number of radial grooves, which in this embodiment of my invention are four in number and are positioned at right angles to each other, the

end of certain of said grooves being shown at 22, in Fig. 1, and the other grooves being formed with relation thereto as indicated. W ithin each of said grooves is arranged the upright portion of the spoke orlug of one of the gear segments. In Fig. 2, two of the spokes or lugs of said gear segments are represented as positioned within the corresponding diametrically arranged grooves.

The drive shaft 4, as shown in Figs. 2, 3 and 6, is provided with a hub 23 loose whereon is a gear 2 1, herein termed a driven element and from which power may be conveyed in any suitable manner, as by means of a gear 25 meshing therewith. It is apparent, however, that the driven element, of any selected character, may be arranged in any proper manner to take power from the transmission ring or rings, which themselves are driven elements; and also serve to connect said segments with the adjustable eccentric disk 8. Thus through their spokes or lugs the segments are operatively associated with a driven element, namely, the ring 18 and also through said spokes or lugs and through said ring 18 are operatively associated with the adjustable eccentric. As represented most clearly in Fig. 2, that face of the gear 24: that is adjacent the right hand transmission ring 18, viewing Fig. 2, is provided with a diametral groove 26, and in the adjacent face of the transmission ring 18 is a similar diametral groove 27 (see Fig. 1) arranged perpendicular to the groove 26. Positioned between the driven gear 24 and the transmission ring 18 is a so-called unison ring 28 having opposite lugs 29 received within the diametral groove 26 and intermediate lugs received within the diametral groove 27, whereby circumferential m v ment is conveyed from the transmission ring 18 to the driven gear. Instead of the unison ring or rings, I may employ any means for conveying movement from the transmission ring to the ultimately driven element, provided such means conveys movement uniformly, that is, provided such means does not vary or alter in transmission the speed of movement imparted to it by the transmis sion ring, which imparted speed or movement varies with each adjustment of the adjustable disk hearing.

I have thus far described the preferred construction of parts involving one set of elements, or that shown in Fig. 2 at the right of the driven gear 2-1:. The construction of parts making up the second set of elements or that shown in Fig. 2 at the left of the driven gear 2%, when a second set of elements is employed, may be and preferably is substantially identical with that already described. In Figs. 9 and 10, I have repre sented the segments 0/, b, 0 and d of the second, or left hand set of elements viewing Fig. 2, and it will be noted that in the Ill) lflll position of parts represented in Figs. 7 and 9 the gear segments a, Z), c and d are arranged respectively at an angle of to the segmental gears a, b, c and (Z. Moreover the diainetral groove in the opposite or left hand face of the driven gear 24 is perpendicular to that shown in the right hand side and consequently the diametral groove in the adjacent face of the left hand transmission ring is normal to that in the right hand transmission ring. The grooves 22 in the outer face of the left hand transmission ring for the reception of the spokesor' lugs of the gear segments a, b, 0 and d are re spectively at an angle of 45 to the similar grooves 22 in the face of the right hand transmission ring 18, as indicated in Fig. 1. It will be understood that the number of grooves in the several parts and their angular arrangement will be varied in different embodiments of my invention, in accordance with the number of gear segments employed.

Having reference first to Fig. 7, it will be apparent that when the shaft L is rotated clockwise the fixed disk bearing 8 will gyrate about said shaft in the manner of an eccentric with the gear segments thereof consecutively meshing with the internal fixed gear or annular rack 15. The said fixed disk bearing 8 rolls about the inner face of the internal fixed gear or rack 15 with the said gear segments in mesh witl the latter, and were the said fixed disk bearing provided with an uninterrupted gear the teeth thereof would constantly mesh with those of the said internal gear or rack. Inasmuch, however, as the gear segments are 'preferably spaced substantially as shown,

and as neither set of said segments in itself makes a complete gear, it is apparent that the said gear segments intermittently and consecutively engage the said internal gear or rack. Inasmuch as the shaft is rotated clockwise, as indicated by the arrow in Fig. 7, each gear segment a, 7), c or (Z, as it engages with the internal gear or rack 15 will be driven contraclockwise as indicated by the arrow adjacent the gear segment a in Fig. 7. This movement of the ear segment r eontraclockwise is imparted by the spoke or lug of said gear to the transmis sion ring 18, and thence through the unison ring 28 or other suitable connections to the drive gear .34; or other driven element, thereby driving the same in a direction opposite to that of the direction of movement of the driven shaft it is, of course, evident that the drive shaft lmay be rotated in either di rcetion, the driven gear 24 being thereby rotated in an opposite direction, in that relation of the iarts thus far described.

Viewing Figs. 7 and 9, it will be noted that in this embodiment of the invention the gear segments 0., Z), c and d and a, Z), c and (Z complementally arranged with respect to each other, so that the two sets of gear segments together constitute substantially a complete gear.

is previously stated, the disk 8 is of a fire-u or unvarying eccentricity. The eccentricity of the disk 10 may be rendered that of the disk 8., or it may be made different therefrom to any extent within the limits imposed by the capacity for adjustment of the disk 10, being made greater or less than the same desired. lVithin the scope of my invention the disk 0 may be adjusted to any desired extent. thus varying its eccentricity to any desired degree. if the adjustable di 10 be so positioned upon its seat that it is of the same eccentricity as the fixed disk 8, then the transmission ring 18 is of the se le eccentricity as said fixed disk 8, and upon rotation of the drive shaft & in either direction the fixed disk 8 rolls about within the internal gear or annular rack 15 with the gear segments thereof meshing therewith, but with. the consequent reverse rotation of the saidgear segments and consequently with the reverse rotation of the driven gear 2d at speed which is the same as that at which the gear 24: would be drivenwere the said eight segments Z 0, d and a, 7), o, d assembled in fixed relation to constitute a single complete gear rolling about and meshing with the internal gear or rack If the. eccentricity of the disk 10 exceeds that of the disk 8, then the speed of the gear 24: is increased over that just referred to and if it be less than that of the disk 8, then the speed of the gear is less than that above indicated.

In Fig. 7. the center of rotation of the shaft 4 is indicated at A. while the centers of the fixed disk bearing and the adjustable disk bearing and its transmission ring are represented at The several gear sen ments at, 7), c, and (Z are so related to each other that axial lines drawn through them and their spokes l6 intersect at the centers of said fixed disk bearing 8 and the adju t able disk bearing 10, with the previously stated result of driving the gear 24 at a speed equalling that obtained by rolling a gear composed of said eight segments in fixed relation within and meshing with the fixed gear 15. Preferably the parts are brought into this relation as a preliminir i to obtaining the desired speed. Such eccentricity may be varied by iz'ioving the slotted disk hearing it), viewing Fig. "2', upward to obtain a still greater speed of the gear 2-11: or downward. viewing said 7. and hence toward the position shown in Fig. 8. this downward movement being of any desired extent within the capacity of the mecha nism, to obtain the desired diminution of speed of the driven gear 24.

When the centers of the fixed disk hearing and the adjustable disk hearing are the same, there'is as described gyratory inmoment of said parts, resulting in the reverse driving of said segment and consequently of the gear 24.

As, however, the eccentricity of the ad justable disk bearing 10 is made different from that of the fixed disk bearing 8 by moving the former toward the center of the shaft 4; or toward the point A in Fig. 7, the result is to enforce a new position of the transmission ring 18, the unison ring adapting itself to any position of adjustment. The adjustment of the disk bearing 10 and consequently of the transmission ring 18 :ompels a repositioning of the gear ulClltS (1,, Z), c and (Z upon the annular liange 8, as indicated for example in Fig. 8, where, however, the adjustment is carried so far as to compel the rotation of the gear 241- in the same direction as the shaft 41, as will be more fully explained. This repositioningof the gear segments is due to the fact that the downward movement of the transmission ring 18 enforces the downward movement if those spokes or lugs 16 of the gear segments that do not occupy a vertical position. Viewing Fig. 8, it will be apparent that the lugs or spokes of the gear segments I), (Z have been moved bodily downward carrying with them said gear segment I), d, but that said lugs orspokes are still horizontally ar ranged and that an axial line drawn therethrough intersects in the shaft 'las in F than axial line drawn through the lugs or spokes of the gear segments a, 0.

The positioning of the adjustable disk bearing 10 so as to make its eccentricity difterent from that of the fixed disk bearing 8 institutes a secondary or neutralizing gyration of said adjustable disk bearing 10 which neutralizestoagreater or less extent that of the still continuing prin'iary gyration of the fixed disk bearing 8, the extent of the neutralization being dependent upon the extent of the change in'position of the adjustable disk bear-mg 10, the result being the rotation of the driven gear 24' still in the reverse direction to that of the drive shaft of that of the shaft 4, or, in other words, the

less will be the rate of rotation of the transmission ring 18. The greater the differential between the primary and secondary gyrations, the greater the difference in speed I of the driven gear 24 with respect to the drive shaft at. If the disk bearing 10 be moved until it is in concentricity with the center of rotation of the driving shaft l, then the gyration of the disk bearing 10 wholly ceases and therefore said disk wholt 1y neutralizes that of the main or primary gyrat-ion of the fixed disk bearing 8, because of the now existing differential between the movements of the fixed and adjustable disk bearings, thereby causing the main drive shaft 4; to rotate without any driving effect upon the gear 24. If this adjustn'ient otthe bearing disk 10 be continued in the same di rection until the transmission ring he shifted so that its center is at the other side of the axial center of the driving shaft 4 (that is, below the said axis of the said shaft when viewing the drawings) then there is instituted a secondary gyration which is not a neutralization of but is supplemental to the main or primary gyration of the fixed disk bearing 8, with the resultthat the gear is now driven in the same direction as the driving shaft 4 but at a speed dependent upon the amount of such secondary but now supplementary gyration. The speed of rotation of the gear 24L in the same direction as the driving shaft 4; is dependent merely upon the extent of adjustment of the disk bearing it) or in other words the extent of adjustment of the .center of the transmission ring below that of the shaft-,4, viewing the drawings, and in the various embodiments of my invention may be made as great as desired' Thus my invention contemplates the reverse driving of the gear 24 at any speed and the forward driving of said gear at any speed, with adjustment of the parts to effect any intermediate speed of said gear 2a in either direction.

In Fig. 7, l have illustrated the position of the gear segments (a, Z), c and d at one position of'adjustment of the bearing disk 10, the near segment a being then in mesh with the nxed internal gear or annular rack 15, with the resiiiltant movement of said gear segment a contraclockwisc. The continued rotation of the drive shaft l clockwise rolls the said fixed disk bearing 8 about within said internal gear or animlar rack and during such movement of the shaft the gear segments 0, 7), c and (Z come successively into mesh with said internal gear 15, thereby compelling continued rotation of said gear 24.

Comparing diagrams 11 to 18 inclusive with diagrams 19 to 26 inclusive, it will be apparent that upon the described rotation of the shaft 4: in a clockwise direction, as the gear segment (1 moves from its position of engagement with the internal gear 15 as illustrated in Fig. 7., the gear segment 0, is brought into mesh therewith, and that as it in turn is with drawn from such engagement the gear segment I) is brought into engagement this action being continued with the segments 5. c, 0, (Z, (Z in the order named. The result 1 an engagement with the internal 15 ot one or more of all the gear segments at all times, the gear segment-s being oi such extent that before one segment is withdrawn from such engagement another is brought thereinto. The employment 0t gear segments permits the true rolling action 01 :uccessive segments into and out ot en einent with the fixed, internal gears 15. comparing; Figs. 8 and 10, it will be evident that whatever he the adjusted eccentricity oi the bearing disk 10, the resultant positions of the segments a, b, 0, a, and a are such that one of said gear 0 c, 4%? segments is constantly in mesh with the internal gear 15, thereby compelling a constant rotation of the driven gear 24. After a gear segment is withdrawn from engagement with the internal gear 15, its subsequent position upon-the flange 9 is immaterial until it is again brought into mesh with said internal gear. it matters not that in certain positions of adjustment a gear segment of each set is in mesh with the internal gear 15, nor that in certain positions of adjustment the gear segments of one set or the other be spaced a ge: er distance apart than in other positions of adjustment, for whatever be the position ot adjustment, the gap between adjacent gear segments of one set is always bridged by gear segment of the opposite set, thereby compelling continuous rotation of said driven gear 24.

In F1, the center 0t rotation of the fixed disk hearing 8 is indicated at X, and the center oi. rotation ot the adjustable disk bearing 10, and the transmission ring is indicated at Y, while the center of rotaiion ot the d living shaft 4 is indicated at The cir 'le X passing through the center 0:"? rotation )1. oi"- the fixed disk bearing in dicates the circular path of travel of the said tired disk bearing, while the circle Y passing thro 1 the point Y indicates the circular path ot travel 01 the adjustable disk hearing. The corresponding points X Y and corresponding circles X Y in Figs. 11 to 13 inclusive and Figs. 19 to 26 inclusive represent the centers of rotation anc paths of travel of the fixed disk hearing and ijustahle disk bearing through one their movement. As the circle Y decreases in radius, owing to the further adjustment of the disk bearing 10, the rate rotation of the driven gear 24 becomes less and less and finally when the circle Y, or path of travel. thereby indicated, vanishes or merges into the center of rotation Z, of the drive shaft 4, the rotation oi the driven gear 24 in a direction contrary to that of the shaft 4 is wholly neutralized so that said gear becomes stationary. This position of forward rotation of the driven gear 24, or,

in other words, a rotation thereof in the same direction as the driving shaft 4.

From the toregoing description, it will. be understood that the gear segments always travel in the same gyratory path with relation to the fixed disk bearings S, inasmuch as they are carried by the circumferential flanges 9 of the fixed eccentric disk bearings 8. During such gyratory movement, they roll around within and in mesh with the fixed internal gears 15. The speed of the shaft and eccentrics is always the same, and when the adjustable eccentrics 10 are of the same eccentricity as the fixed eccentrics 8, then, as previously stated, the resulting speed of the driven gear 24 equals that derived from complete gears rolling within and in mesh with the said internal gears. By altering the eccentricity of the said adjustable disk bearings 1.0, however, the circular path of movement of the centers of the said. disks 10 is increased or decreased in diameter according as the e centricity of said disks is increased or diminished. If the circular path of movement of the centers of the eccentrics 1O equals that of the centers of the eccentrics 8, as stated, the resulting speed is that of complete gears rolling in mesh with the fixed internal gears 15, but it the circular path of the centers of the eccentrics 1O exceeds that of the centers of the eccentrics 8, the resulting speed is greater, and it the disks 10 be brought into concentricity with the shaft 4, the circular path of movement of the centers of said disks 10 is reduced to a point or disappears with the result that no driving movement is imparted by the said disks 10 to the gear 24.

The pinion or pinions 13 may be rotated in any suitable manner to adjust the eccentric disk bearings 10. Herein as shown in Fig. 3, a single elongated pinion 13 is employed to adjust both disk bearings 10. In order to rotate the pinion 13, I have, in Figs. 1, 2, 3 and 4, represented a handle 31 provided upon a disk 32 having a hub 33 mounted in a standard 34 having therein a segmental slot 35, with which engages a bolt or set screw 36 permitting any desired adjustment of said disk 32 and handle 31. Herein shown as having a tongue and groove guiding engagement with the disk 32 is a nam ng. 3, said p} cured"fixedly!ih osition is provided externally as iii Fig.

casing or frame 37 keyed to the shaft 4: and having an internal gear or annular raclc Keyed upon the spindle of the adjustmg pinion 13 is a pinion 43 to which I impart one revolution for each revolution of the in ternal gear 38, in order that the relative circumferential positions of said pinion and gear may remain unaltered during the ro tation of the drive shaft l, until it is desired to re-adjust the position oi? the eccentric disk Any suitable gearing may be bearings 10.

employed for the purpose. shown a gear 39 keyed upon a sp ndle 259 f mounted upon a bracket 10 extending l'rom' the disk 32;

Said gear 39 is one half the diameter of the internal gear 38 and meshestherewithi Formed with or fast upon the spindle" 39" is a pinion ll meshing with a pinion loose upon a stud extending from the disk :52, and meshing with said pinion 4:3, oi. wh ch it is one half the (immerse Upon circum-j ferential adjustment of the disk 32 by movement of the handle 31 the gear 39 is rolled within and upon the internal gear 38 and; through the described train of gearing im parts rotative movement to the pinion l3, and hence to the elongated pinion 13 relative to the driving shaft at, thereby altering the adjustment of the eccentric disk bean" ings1'0 to the extent desi ed.

I'have heretofore referred to gear or gears 15 as fixed. do not intend to preclude their capacity for adjustment. It may be desirable cir::um-' ferentially to adjust said internal gears, as for instance to avoid the necessity of torming said gears with special teeth. In other words, at the commencement of the operation when one of the segmental gears is about to engage with its internal gear, in which case the parts may be positioned substantially as shown in Fig. 11., it would be necessary in this embodiment oi. my invention to provide the internal gears with a special form of teeth, unless it were possible circumferentially to adjust said internal" gears to permit the proper meshing of the teeth of the gears 15 and the first gear segments.

Any suitable means may be em :)loycd cir-' 'cumferentially to adjust said internal gears In Figs. 33'and 34, I have shown means for number of teeth 44:, with which meshes av worm 45 upon shaft 46 provided at its upper end with a hand wheel l7. Said shaft is mounted in suitable hearings in brackets 4L8t8 extending from the standard 2. Preferably I provide means simultaneously to adjust the internal gear or gears 15 and the elongated pinion 13 controlling the position of the adjustable segments 10 to main tain the proper relation of the parts. To this end, I may omit the handle 31 froni the disk shown. in. Fig. 4. and in lieu thereof provide the shaft 46 with a beveled pinion 49 meshing witlra beveled gear 50 fast upon a shaft 51 mounted in a bearing in the standard 2 and provided upon its op posite end with a pinion meshing with a gear 53 formed upon the periphery of the disk 32. It is apparent that by turning the hand wheel 47 the internal gear 15 may be rotated to the desired extent to adjust the same with respect to the segmental gears and that simultaneously the position of the adjustable segments 10 may be alterec. thereby to produce the desired speed of the driven gear 24. In the embodiment of my inveir tion herein described. and wherein two internal gears 1.5 are employed, I provide suitable mechanism circumferentiallyto adjust both of said gears. If desired such mechanism may be connected for simultaneous op-' eration so that but a single hand wheel 47 or the like is necessary.

In the device illustrated herein the driving belt is applied to the driving pulley 5', wh ch. with its shaft 4, eccentric bearings 8 and 19'. and cooperating internal gear 15, transmit rotary motion to and through the other parts of the device, hence said driving pulley, its shaft, and the eccentric bearings niavtogether be considered as the driving element, or any one of them might be 50 considered, upon the understanding that the effective axis 01" said driving element is that which transmits motion to the gear segmei Said effective axis is a resultant of the fixed eccentricity ot the bearing 8 and the adjustable eccentricity of the bearing 1.0 as heretoiore described, and is adjustable as to its path of movement according to the adjustment of said eccentric bearing 10. In other" words. the cfl'ective axis of the. driving 'member' or group of members constituting Herein I have the internal By this term I effecting this result, it being understood that f'wliat I have herein referred to as the driving by the same or similar means both internal gears shown in this embodiment of my in-" ventitin may 'thus be adjusted, This de} sirability of circumferential adjustment par- 7 ticularly arises in the case of the use of a" plurality of fixed internal gears, such as 15.

Referring for purposes of description."

element otthe device, is the gyrating axis about which are grouped the pivot pins 17 of r the gear segments (ii-03 and ld", a resultant of the relative adjustment of the axes of the eccentric bearings 8 and 10, which lattr are upon, moved with, and together determine the effective axis of the driving element of merely, to that'internal gear sl'iown at thew t the device.

gear instead ofb'eina e.-

In the device illustrated, power is taken trom the transmission rings or straps 18 34 with a suitable -through the unison rings'28and. the gear lit-3 24, and said members together or separately may be considered the driven element of the device; the axes of said driven rings 1.8 and of the driving element heretofore mentioned are relatively adjustable into positions of greater or less relative ec*cntricity.

(lperatively interposed between the driving and driven elements are the groups of segmentally shaped members or toothed gear segments, (i-(Z and ((Z which serve to transmit motion and power from the driving element to the driven clement. Each such toothed gear segment together with its spoke or lug l6 and pivot pin 17 may conveniently be termed d1. 7 gunit for transmitting motion from the driving to the driven elements. The driving units of each group are disir buted in a single plane about the axes of the driving and driven elements and are operatively connected with one of said elements. herein the driving element, in a crank-like manner, that is to say, the driving units are moved by the drive shaft and eccentrics and the connections therewitl'i in the manner of a crank which furnishes the connection between said driving element and the driving unit or units.

In any adjusted position of the adjustable eccentric bearings 10, whether of greater or less or the same eccentricity as the fixed eccentric bearings, the outer end of each driving unit where the teeth of a segment engage the internal teeth of the gear 715, makes intermittent engagement with said gear and the points of such intermittent engagement change or are adjustable around the pitch line circle or circumference thereof since at each succeeding engagement said r-aegment engages a new tooth or teeth more or less removed from that or those previously engaged. the points of engagement progressing around the said gear 15 in steps determined as to the period, spacing, or rapidity of engagement according to the extent of the relative eccentricity above mentioned.

ln engaging and disengaging from said gear 15 each driving unit approaches and recedes from said member in a rolling manner, that is to say, the action is such that the two members, so to speak, roll to- ,ccther and away from each other; not only the action of meeting and receding thereby made easy and susceptible of ready and effective guiding, but the period of eifective. normal driving contact or engagement between the same may thereby be prolonged. Such engagement and disengagement of the effective driving parts relieves the same. of unnecessary frictional engagement between successive points of intermittent engagement and renders also the adjustment of the transmission from one to another speed more easy, mechanical and efficient. Thus, while the engagement is intermittent,- it

varies in duration according to the extent o2 S=i1l relative eccentricity above mentioned and lg to the variation of transmisaccom sion obtained thereby or therefrom.

An important characteristic of the transmission device described is that the driving action or thrust of the driving unit to and upon the engaged element is in a line normal to the abutment or thrust-receiving face on said element with which it is engaged during the driving period; in the present instance that abutment face is the effective face of the internal tooth or teeth on the annular member or gear 15 with which the driving unit, for the time being, in engaged. An arrangement that permits the driving thrust to be delivered upon the abutment face of the engaged element in a line normal or substantially normal to said face. renders the device positive in its action and free from heat generating conditions that characterize an ordinary clutch or gripping arrangement for delivering a driving thrust from the driving unit to the member ongaged thereby.

If the driving thrust were exerted in a direction not normal to the abutment face of the element engaged by it, the moment the angle of repose at either side a line truly normal to that abutting face he passed, the driving thrust would tend to produce a lateral slipping action between the driving unit and said face, which would require resistance by some friction clutch or other device. So long, however, as the driving thrust is within the angles of repose at the sides of a line truly normal to the abutment face, said line of thrust may be said to be substantially normal to said face and may be employed as freely as if it were a true normal to deliver positive driving force from one part to its engaged part without liability to lateral slip and without requiring any supplementary clutches or other devices to maintain the engagement.

here the drivin units and engaged elements are provided with gear teeth, s in the.

present instance, the'range of adjustment in speed due to the relative adjustment of the effective axes of the driving and driven elements would be limited to a step adjustment and to a maximum number of steps between speed ranges dependent upon the size and number of teeth, were it not that in the present instance the adjustment is rendered truly universal so that any intermediate speed may be obtained from minimum to the maximum in either direction due to the adjustability of the internal gear or gears 15 upon their own axes, as by the means shown in Figs. 33 and 34. By so adjusting said gears circumferentially and relatively to the segments the proper engagement therebetween is assured in any adjusted position of the eccentric bearings. Thus the intermitlll) iii

tent rolling engagement of said segments and gear is made universally adjustable circumferentially about the axis of said engagedgear or member throughout. a complete circle.

Each of the segments or driving units in its movement toward and from its engaged element moves in an endless path until the limit of movement is reached, where it moves directly radially in a straight line as stated, and whatever its movement, whether in a straight line or in an endless path, the driving units at their effective driving portions approach and recede from the engaged element in a general direction that is substantially normal to that elementiii the region of that engagement.

As already observed, the points of engagement of the driving units with the engaged element shift variably around the lat ter according to the path of movemcnt of the effective axis of the driving eleinlint, and according to the extent of relative eccentricity of the axes of the driving element and the driven rings 18; as the said relative ec-- centricity is varied, the radial position of a driving unit with respect to the axis of the driven element when such unit is driv ing is also varied, as well as the speed transmitted.

The driving units and gear 15 whether actually engaged or for the time being disengaged, are always in juxtaposition where 1 they may be readily guided into the next engagement by suitable means as here provided. in the present instance it will be observed that during the periods of actual disengagement between the teeth of the segments and the element that is engaged thereby said segments are positively held or guided by the annular flange 9.

Having thus described one illustrative of toothed gear segments distributed about said shaft, gyratorially acting means upon said shaft and supporting said segments for angular movement about said shaft, said means'being effective to vary the radial position of one or more of said segments with respect to said drive shaft, a toothed gear surrounding the shaft and with which said segments are adapted. to mesh, and driving connections between said segments and said driven element.

2. Speed varying mechanism comprising .in combination driving and driven elements,

the former including a drive shaft, transmission members thereon of fixed and adjustable eccentricity respectively, a circumferential series of toothed gear segments niovably carried by one of said members and operatively associated with the driven element and with the other of said members, means. to position said adjustable transmission member in concentric or eccentric relation to said fixed transmission member, and a surrounding toothed gear with which said segments are adapted to mesh.

3. Speed varying mechanism comprising in combination driving and driven elements, the former including a drive shaft, a pair of transmissioninemhers supported thereon and of fixed and variable eccentricity respectively, one or more toothed gear segments slidably supported by one and operatively connected to the other of said trans mission members, and to said driven element, and a surrounding toothed. gear with which said segment or segments are adapted intcrmitteiitly to engage. I

4. Speed varying l'llGCllZLlllSll'l comprising in combination driving and driven elements, the former including a drive shaft, a gymtory member of fixed eccentricity upon said shaft, toothed gear segments supported by said member and circumferentially. movable relatively thereto, a toothed gear with which said segments are adapted intermittently to engage, means variably to position said segments about said gyratory member, and connections between said seg-' ments and said driven element.

5. Speed varying mechanism comprising in combination driving and driven elements, the former including a drive shaft, lived and adjustable gyratory transmission members carried thereby, toothed gear segments carried by one of said transmission members and circunitei'entially ITlOVablG relatively thereto, a normally stationary toothed gear with which said segments circumferentially engage and operatiiig connections between each segment andsaid driven element including a ring loose upon the other of said transmission members.

6. Speed varying mechanism comprising -in combination a drive shaft, driving and driven elements respectively fast and loose thereon, fixed and adjustable gyratory transmission members carried by said shaft, one or more toothed gear segments carried by one of said transn'iission members for circumferential movement relatively thereto, means upon the other transmission member variably to position said segment or segments, a toothed-gear to be engaged bysaid segment or segments thereby to move the latter relatively to the transmission mem ber carrying them, and positive connections between said segment or segments and said driven element.

7. Speed varying mechanism comprising in combination driving and driven elements,

the former including a drive shaft, a gymtory member thereon, a plurality of circumferentially movable toothed gear segments carried by said gyratory member, means to vary the circumferential relation of one or more of said segments and said gyratory member, a toothed gear with which said segments are adapted to mesh thereby to cause them to rotate relatively to said gyratory member while gyrating, and positive connections between said segments and the said driven element.

8. Speed varying mechanism comprising in combination driving and driven elements, the former including a drive shaft, a gymtory member thereon, a circumferentially movable toothed gear segment carried by said gyratory member, means to vary the circumferential relation of said segment and said gyratory member, a toothed gear with which said segment is adapted to mesh thereby to cause it to rotate relatively to said gyratory member while gyrating, and driving connections between said segment and said driven element.

9. Speed varying mechanism comprising in combination driving and driven elements, the former including a drive shaft, a gyra tory member thereon, a toothed gear seg ment carried by said member and angularly movable relatively thereto, means to vary the path of movement of said segment, a toothed gear with which said segment is adapted to engage thereby to move the latter relatively to said gyratory member, and connections including a unison ring between said segment and said driven element.

10, In speed transmission mechanism for converting constant rotary to variable speed rotary motion, the combination of a drive shaft, fixed and adjustable gyratory transmission members thereon, toothed gear segments supported for angular sliding movement about one of said members, and operatively connected with and to be moved by the other of said members.

11. Speed varying mechanism comprising in combination a criving element including a drive shaft, fixed and adjustable gyratory transmission members thereon, a toothed gear surrounding said shaft, toothed gear segments supported for sliding movement eircumferentially of one of said transmission members and operatively associated with the other of said members, said segments being adapted intermittently to engage said gear, and a driven element rotatably supported about said shaft, there being positive connections between said segments and said driven element.

12. Speed varying mechanism comprising in combination a drive shaft, fixed and adjustable gyratory transmission members fast thereon, a toothed gear surrounding said shaft, toothed segments 'circumferentially movable upon one of said transmission mem bers, having operating connections with the other of said transmission members, and adapted to mesh with said gear, a driven element loose upon said shaft, and connecting means including said operating connections and a unison ring surrounding said shaft be tween said segments and said driven element.

13. Speed varying mechanism comprising in combination driving and driven elements, the former including a drive shaft, a gyratory element fast thereon, one or more toothed gear segments carried by said gyratory element and operatively connected with said driven element, a toothed gear with which said segment or segments engage thereby to cause them to rotate relatively to said gyratory member while gyrating, means to vary the path of movement of said segment or segments, and means to adjust said gear.

14. Speed varying mechanism comprising in combination driving and driven elements, the former including a drive shaft, fixed and adjustable gyratory members thereon, toothed gear segments carried by one of said transmission members and circumferentially movable relatively thereto, a normally stationary toothed gear with which said seg ments intermittently engage, operating connections between each segment and said driven element and between each segment and the other of said transmission members, and means circumferentially to adjust said gear.

15. Speed varying mechanism comprising in combination driving and driven elements, the former including a drive shaft, toothed gear segments supported by said drive shaft and angularly movable relatively thereto, a normally stationary toothed gear, means cooperating with said drive shaft to roll said segments within and in intermittent driving relation to said gear, and positive driving connections between said segments and said driven element.

16. In speed transmission mechanism for converting constant rotary to variable speed rotary motion, in combination a drive shaft, an eccentric transmission member mounted on said shaft and havinx a flange, and a plurality of gear segments mounted and circumferentially movable upon said flange and relatively to each other, and means to cause said movement of the segments.

17. Speed varying mechanism comprising in combination driving and driven elements, the former including a drive shaft, a surrounding toothed gear, an eccentric transmission member mounted on said shaft and having an annular gear-supporting forma tion, a plurality of relatively movable toothed'gear segments supported by and cir cumterentially movable With respect to said formation and engageable with said gear, and driving connections between said segment or segments and said driven element.

18. Speed varying mechanism comprising in combination operatively connected driving and driven elements, the former including-a drive shaft, an eccentric transmission member thereon, a surrounding toothed gear,

a plurality of circumterentially shiftable toothed gear segment-s upon said transmission member and engageable with said gear, gyratorially acting means to vary the radial position of said segments with respect to the axis of the driven element and driving connections between said segments and said driven element.

19. Speed varying mechanism comprising in combination driving and driven elements, the former including a drive shaft, a transmission member of fixed eccentricity thereon, a surrounding toothed gear, one or more toothed gear segments carried by said transmission member, angularly movable relatively thereto and intermittently engageable with said gear, said segment or segments being connected with said driven, element, and means to vary the relative radial position of said segments and said, driven element whereby said angular movement ot said segments imparts rotation to said driven element at speeds dependent upon said relative radial position.

2t). Speed varying mechanism comprising in combination driving and driven elements, the tormer including a, drive shaft, gyratory members thereon, and ot' fixed and variable eccentricity respectively, a fixed internal gear and connections between said gyratory members and said internal gear and also between said members and the driven element.

2].. Speed varying mechanism comprising in combination a drive shaft, a d 'iven element, and positive gearing connections be tween said drive shaft and driven clement, said gearing being adjustal'ile to effect the driving of the driven element at a greater, or less or equal speed with respect to said drive shatt and in either direction, and also at. any intermediate speed.

2-2. Speed varying mechanism comprising in combination a drive shatt, a driven ele ment loosely supported thereon, gyratory members upon said sliatt andot' .tixed and variable eccentricity respectively, and driving o'mnections between said members and said (lI'lVLD GlGll'HIli, said connections'in eluding a circum'lerential series of toothed gear segments slidably supported on one of said gyratory members and slidable by the other oi said members, a toothed gear with which said segments are engageable, and radially movable blocks between said segments and said driven element.

23. Speed varying mechanism comprising in combination driving and driven elements, the former including a drive shaft, a gyrator-y member thereon, and a coacting series ojt toothed gear segments angularly movable upon said gyratory member; a normally stationary toothed gear with which said segments are adapted torintermittent rolling engagement, positive driving connections between said segments and said driven element to impart rotation to said driven element, and means to vary relatively to the axis 0t said driven element the radial position of said segments when in engagement with said gear.

2 L. Speed varying mechanism comprising in combination driving and driven elements, the tormer including a drive shaft, a surrounding toothed gear, gyratory members on said shaft, an adjustable member to modity the action of one o'li' said gyratory members, a circumferential series ot toothed gear segments supported tor angiilar movement upon the other at said gyratory members and adapted. to mesh with said gear, a ring-like member loose upon said mentioned gyratory member and positive driving connections between said segments and said ring-like member, and between the latter and said driven element.

Speed varying mechanism comprising in combination a drive shatt, driving and driven elements respectivel' fast and loose thereon, primary and secondary gyratory transmission members upon saidshatt, means to modify the action of said. secondary gyratory transmission member, a circumferential series of toothed gear segments angularly movable about the axis oi said primary gyratory transmission member, a toothed gear with which said segments are adapted tor intermittent rolling engagement, a ring-like member loose upon said secondary transmission member, and positive driving connections between said segments and said. ring-like member and between the latter and said driven element.

26. Speed varying mechanism comprising in combination a drive shaft, a driven element, positive gearing connections between said drive shaft and driven element, said gearing being adjustable to ettect the driving of the driven element at a greater or less or equal speed with respect to said drive shaft and also at any intermediate speed.

In testimony whereof, I have signed my name to this specification.

BICKNELL HALL. 

